Feedback mechanism for variable displacement hydraulic device having an electrohydraulic controller

ABSTRACT

Mechanical feedback through an articulated mechanism is provided between the swashplate of a variable displacement hydraulic device and the output stage of an electrohydraulic servovalve for controlling such swashplate.

This is a continuation of pending application Ser. No. 869,829 filedJan. 16, 1978 now abandoned.

FIELD OF THE INVENTION

This invention relates to the field of electrohydraulic controlmechanisms for variable displacement hydraulic devices as used inhydrostatic transmissions.

BACKGROUND

Variable displacement hydraulic pumps and motors are often used as arugged, reliable and convenient way to transfer drive shaft power in acontrolled manner. Such hydrostatic drives are used in constructionvehicles and equipment, agricultural machinery, materials handlingequipment, maritime vessels, machine tools, garden tractors andrecreational vehicles.

In the usual application, a variable displacement pump is driven by apower source, such as a diesel or gasoline engine, turbine or electricmotor. Flexible hydraulic lines or hoses connect the pump output to ahydraulic motor that drives the load.

In some instances in the past, pump displacement has been controlled bya manual lever throughout the range from zero to full flow in eitherdirection. This provided an infinitely variable transmission ratio tothe load, from full forward to full reverse, without the use of aclutch, mechanical gear box, or other functionally equivalent mechanism.

In such an arrangement, the hydraulic motor can be conveniently locatedat the load, while the pump is proximate the power source. Thetransmission ratio can be changed quickly by mere manipulation of thecontrol lever, without damage to the pump or motor. Full load torque isavailable at stall, and optimum engine speed can be maintained at alltimes.

In one prior art form of hydrostatic drive, the pump was a variabledisplacement piston pump having a pivotal swashplate for determining thelength of stroke of the pump piston. The angle of this swashplate wasset by a lever manually controlled by the operator to displace a controlvalve for regulating flow to a control piston which positioned the angleof the swashplate and thereby regulated the desired load speed. Often aseries of levers, push rods, bell cranks, or cables, were used toconnect the operator's control lever to the pumps stroking mechanism.

In order to eliminate such mechanical interconnection between theoperator and the hydrostatic pump, a simple potentiometer was locatednear the operator to selectively provide an electrical command signalfor an electrohydraulic servovalve which was substituted for the formercontrol valve. Thus, an electrohydraulic control mechanism replaced themanual lever and control valve and acted to position the swashplate inresponse to electrical commands. Feedback of swashplate position to thetorque motor of the electrohydraulic servovalve was either mechanical asby a lever and spring operatively interposed between the swashplate andthe movable armature of the torque motor, or electrical as by apotentiometer operatively interposed between the swashplate and thecoils of the torque motor so that a negative feedback signal responsiveto the position of the swashplate was generated to be algebraicallysummed with the electrical command.

SUMMARY OF THE INVENTION

The present invention provides a feedback connection between the pivotalswashplate and the output stage of the electrohydraulic servovalve,rather than its input hydraulic amplifier or torque motor stage as wasdone heretofore. This is achieved by providing a servovalve which has anoutput stage including one flow control member movable in response toangular movement of the swashplate. Preferably, this member is ametering port member, such as a ported sleeve, which is movable relativeto a second output flow control member, a movable valve element, such asa valve spool, surrounded by such sleeve. This provides mechanicalfeedback from the pump stroking mechanism on a one-to-one follow-upbasis. When there is relative displacement between the output flowcontrol members, hydraulic fluid is ported to the pump stroking pistonto cause the relative displacement to approach zero.

This inventive arrangement provides a simplified mechanical feedbackmechanism between the pump swashplate and the servovalve, by effectingfeedback through a single lever and eliminating the need for feedbacksprings.

An important object therefore is to provide a simplified mechanicalfeedback mechanism between a pivotal swashplate of a variabledisplacement hydraulic device and the output stage of anelectrohydraulic servovalve controlling the flow of fluid to thestroking mechanism.

Another object is to provide such a mechanical feedback mechanism whichis rugged.

A further object is to provide such a mechanical feedback mechanismwhich can be immersed in hydraulic fluid and therefore can be utilizedwith an electrohydraulic servovalve of the dry torque motor type withoutsacrificing the advantages thereof, by arranging the feedback mechanismon the wet side of a flexible barrier in such type of servovalve whichisolates the motor on the dry side of the barrier.

Yet another object is to provide such a mechanical feedback mechanismwhich converts pivotal motion of the swashplate to translationalmovement of the metering port element while accommodating the angularityof this motion conversion.

Other objects and advantages of the present invention will be apparentfrom the following detailed description of a preferred embodimentillustrated in the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic illustration of an electrohydraulic controller inassociation with a hydrostatic pump and embodying the improvedmechanical feedback mechanism of the present invention, the position ofthe pump being shown for no electrical input to the controller.

FIG. 2 is an enlarged fragmentary transverse vertical sectional viewthereof taken generally on line 2--2 of FIG. 1, and showing a trunnionfor the swashplate illustrated fragmentarily and in section, and alsoshowing the electrohydraulic controller mounted proximate such trunnionand illustrated principally in elevation but with portions broken awayto reveal the elements of the inventive mechanical feedback mechanismoperatively interposed between the swashplate and output stage of thecontroller.

FIG. 3 is a still further enlarged fragmentary view of the portion ofthe controller output stage and feedback mechanism within the area shownbroken away in FIG. 2.

FIG. 4 is a fragmentary vertical longitudinal sectional view thereoftaken generally on line 4--4 of FIG. 3, and showing the spaceaccommodation for arcuate movement of the feedback arm carried by themetering port sleeve.

FIG. 5 is a similar fragmentary vertical sectional view transverse ofthe sleeve feedback arm, taken on line 5--5 of FIG. 3, and showing theeccentricity of this arm's connection to the pivotal feedback lever.

FIG. 6 is a fragmentary horizontal sectional view thereof, takengenerally on line 6--6 of FIG. 3, and further illustrating the ball andrecess type connection between the feedback lever and arm.

FIG. 7 is a schematic illustration of the electrohydraulic controllershown in the upper portion of FIG. 1, and depicting the displacement ofthe valve spool relative to the metering port sleeve which takes placeinitially upon an electrical input to the controller to effect a fluiddrive of the stroking mechanism before the swashplate is displaced fromits position shown in FIG. 1.

FIG. 8 is a schematic illustration of the apparatus shown in FIG. 1, butdepicting the condition of the output stage of the controller afterfinal displacement of the swashplate in response to the effect of anelectrical input to the controller as depicted in FIG. 7.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

It is to be understood that like reference numerals used throughout thedrawings and ensuing description are intended to indicate the sameelements.

The inventive mechanical feedback mechanism is shown in the drawings asoperatively interposed between a variable displacement pump 10 and theoutput stage of an electrohydraulic controller 11. This pump andcontroller are illustrated schematically in FIG. 1.

Pump 10 is shown as having a stationary housing 12 surrounding arotatable cylinder block 13 adapted to be rotated by a shaft 14 drivenby any suitable prime mover or power source (not shown). The cylinderblock is shown as having a pair of pump pistons 15, 15 severallyarranged on opposite sides of the drive shaft, each having a rod 16carrying a pivotal shoe 18 at its outer end. These shoes 18 bear againsta swashplate 19 on opposite sides of its pivotal axis, indicated at 20,which extends transversely to the longitudinal axis of drive shaft 14.Pump output flows through output passages 21, 21 which are suitablyconnected to a hydraulic motor (not shown).

Means are provided for setting the angular position of swashplate 19about its axis 20. As shown, such means include a control piston 22 in acylinder 23 provided in pump housing 12 on one side of axis 20, and asimilar control piston 24 in a cylinder 25 provided in the pump housingon the other side of axis 20. Each piston 22, 24 has a return spring 26.Cylinders 23 and 25 are served hydraulical by ports 27 and 28,respectively. A link 29 connects piston 22 to the upper part of theswashplate above its pivotal axis 20, and a similar link 30 connectspiston 24 to the lower part of the swashplate below this axis.

By controlling differentially the flow of hydraulic fluid through ports27 and 28, control pistons 22 and 24 can be positioned in theirrespective cylinders to set the angle of swashplate 19 and therebycontrol the length of stroke pump pistons 15 will have, to regulate theflow through pump ports 21. Such a pump stroking mechanism, includingthe pump itself, is well understood by those skilled in the art.

Electrohydraulic controller 11 is shown as an electrohydraulic flowcontrol servovalve having a hydraulic amplifier 31 of the doublenozzle-flapper type, and as also having an output stage 32 including arectilinearly-movable valve spool 33, with mechanical feedback betweenthis spool and flapper. Such a mechanical feedback flow controlservovalve is more fully illustrated and described in U.S. Pat. No.3,023,782 the disclosure of which is herein incorporated bycross-reference.

Suffice it to say here, that hydraulic amplifier 31 includes a flapper34, and a pair of stationary nozzles shown as right and left nozzles 35and 36, respectively. Pressurized fluid is supplied to these nozzlesupstream of their discharge openings from a suitable source (not shown)external of valve body 37, via a first supply passage 38 connected bybranch passage 39 having a restrictor 40 therein to right nozzle 35, andvia a second supply passage 41 connected by branch passage 42 having arestrictor 43 therein to left nozzle 36.

The servovalve 11 is also shown as having a torque motor 44 includingupper and lower pole pieces 45 and 46, respectively, separated toprovide air gaps 48 in which the opposite ends of a horizontal armature49 are arranged. These pole pieces are associated with permanent magnets(not shown) so as to polarize them. This armature is centrally fixed tovertically disposed flapper 34 to provide a rigid T-shaped member whichis supported on a frictionless pivot having an axis indicated at 50,provided by a flexure tube 51 which surrounds the flapper in spacedrelation thereto. The lower end of flexure tube 51 is suitably sealinglysecured to valve body 37 and the upper end of this tube is suitablysealingly secured to the armature-flapper member. Each arm of armature49 is shown as surrounded by a coil 52 so that when energized through asuitable circuit (not shown), well understood by those skilled in theart, an electromagnetically induced flux can be produced in the air gaps48 to attract armature 49 closer to one than the other of the portionsof the pole pieces at each air gap and thus pivot the armature-flappermember about axis 50. The tip of flapper 34 is movably arranged betweennozzles 35, 36 which discharge hydraulic fluid thereagainst to becollected in a sump chamber represented at 53 connected to a drain port(not shown) in valve body 37.

Differential movement of the flapper relative to the nozzles produces adifferential pressure in branch passages 39, 42 upstream of thedischarge openings of these nozzles. This differential pressure isapplied to the ends of valve spool 33 to control its rectilinearmovement. For this purpose, valve body 37 is shown as internally formedto provide a cylinder 54 in which a sleeve member 55 is slidably androtatably arranged. Each end of cylinder 54 is provided with an annularrecess 56 to accommodate the corresponding end of sleeve 55. Each recessprovides a stem 58 which projects into the corresponding end of thesleeve. The opposing and spaced end faces of these stems and valve spoolprovide a right spool end chamber 59 and a left spool end chamber 60.Right chamber 59 constantly communicates with branch passage 39 leadingto right nozzle 35 through an opening 61 in sleeve 55 and a passage 62in the valve body. Similarly, on the left side, left chamber 60constantly communicates with branch passage 42 leading to left nozzle 36through an opening 63 in sleeve 55 and a passage 64 in the valve body.

Sleeve 55 is shown as having a right supply port 65, on its outsideconstantly communicating with right supply passage 38, and on its insideconstantly communicating with the annular space 66 between a right outerlobe 68 and a right inner lobe 69 on valve spool 33. The sleeve also hasa left supply port 70, on its outside constantly communicating with leftsupply passage 41, and on its inside constantly communicating with theannular space 71 between a left outer lobe 72 and left inner lobe 73 onthe valve spool. Between ports 65, 70 is a drain port 4, on its outsideconstantly communicating with sump 53, and on its inside constantlycommunicating with the annular space 75 between axially spaced innerlobes 69, 73.

Sleeve 55 is also shown as having a right metering port 76 proximateright inner lobe 69, and a left metering port 78 proximate left innerlobe 73. These metering ports constantly communicate with right and leftactuating ports 79 and 80, respectively, in valve body 37. A conduit 81is shown as constantly communicating right actuating port 76 with upperstroking cylinder port 27, and a conduit 82 is shown as constantlycommunicating left actuating port 78 with lower stroking cylinder port28.

In order to provide mechanical feedback between the valve spool 33 andflapper 34, a feedback spring wire 83 at one end is cantilever-mountedon the tip of the flapper, and at its other end is constrained to movesubstantially frictionlessly with the valve spool. For this, the lowerend of wire 83 carries a spherical ball 84 which rollingly engages thewalls of a groove 85 provided in the stem of the valve spool between itsinner lobes 69, 73.

The axial distance between the bottoms of annular recesses 56, 56 isgreater than the axial length of sleeve 55 so that this sleeve neverbottoms out during its full range of axial movement. These recesses aresuitably connected to drain, in a manner not illustrated but wellunderstood by those skilled in the art, to carry away any fluid leakedpast the ends of the sleeve.

The inner lobes 69, 73 of valve spool 33 are shown, as is preferred,underlapped to drain and overlapped to pressure. The underlap, inconjunction with the control piston return springs 26, gives a positiveneutral dead-zone.

In accordance with the present invention, mechanical feedback means areoperatively interposed between swashplate 19 and output stage 32 ofelectrohydraulic controller 11. Such means are shown in FIGS. 2-6.

Referring to FIG. 2, the pump housing 12 on one side is shown as havingan opening 88 closed by a trunnion member 89 secured to the housing asby a plurality of machine screws 90. At its inner end, which projectsinwardly of the housing wall, trunnion member 89 supports a taperedroller bearing 91, on which one side of swashplate 19 is mounted. Theother side of this swashplate is similarly mounted on a trunnion member(not shown) so that the swashplate is pivotal about horizontaltransverse axis 20.

The valve body 37 of controller 11 has a vertical flat inner side face92 which engages the vertical flat outer surface 93 of trunnion member89. Suitable fasteners (not shown) secure this valve body to thetrunnion member.

A horizontal feedback shaft 94 is suitably fixedly connected toswashplate 19 and extends laterally therefrom, concentric with axis 20,through a bore 95 in trunnion member 89. At surface 93, shaft 94 isshown as provided with an enlarged, flat-sided, cylindrical, integralhead 96. Slightly inwardly of the shoulder of this head, shaft 94 has anannular groove in which an O-ring 98 is arranged to sealingly engage thewall of bore 95.

As best shown in FIG. 3, valve body face 92 has a cylindrical recess 99to accommodate shaft head 96, which is rotatable in such recess. Thevalve body 37 is shown as having an access opening 100 which extendsfrom the base of recess 99 to sump chamber 53, this opening beinghorizontal as viewed in FIG. 3 and eccentric with respect to axis 20.Substantially in line with opening 100, a horizontal cylindrical recess101 is provided, partly in the body of feedback shaft 94 and partly inits head 96. Its axis, represented at 102 in FIG. 5, is offsetvertically above feedback shaft axis 20 a distance L FIG. 5 whichrepresents a lever arm.

Sleeve 55 is shown as having a rigid feedback arm 103 projectingradially outwardly therefrom, and horizontally as shown in FIG. 3. Theouter end of this arm has a slightly enlarged spherically-surfaced head104 having a diameter corresponding to that of recess 101 and arrangedtherein and engaging the wall thereof. The inner end of arm 103 is shownat 105 as being externally threaded and screwed into an internallythreaded hole 106 in sleeve 55. This arm also has an integral collar 108at the inner end of the threaded section 105, which, when assembled tothe sleeve, is preferably staked at two places indicated at 109, 109 toprevent rotation of the arm relative to the sleeve.

As seen in cross-section in FIG. 4, access opening 100 is preferablyarcuate in shape to accommodate circumferential tipping of the sleeve 55about its longitudinal axis 110 (FIG. 3) when the sleeve is displacedalong this axis. The vertical displacement of feedback arm 103 in theplane of FIG. 4, due to such tipping of the arm causing rotation ofsleeve 55, is represented by FIG. 5. This corresponds to a horizontaldisplacement X of the sleeve along its axis 110.

During such vertical and horizontal displacements Y and X, respectively,spherically-surfaced head 104 must have a rolling engagement with thecylindrical wall of recess 101, both circumferentially and axially ofthis recess. This is referred to herein as a ball and recess meansconnecting the feedback arm 103 and feedback lever 96.

Referring to the schematics of FIGS. 1, 7 and 8, feedback lever 96 isrepresented by broken line 96', feedback arm 103 by broken line 103',and the ball and recess means connecting them by a dot J representingthis joint.

OPERATION

In explaining the operation, it is assumed that the various partsinitially are in the condition depicted in FIG. 1.

Let it now be assumed that there is an input to the controller in theform of an electrical current to the coils 52 of torque motor 44. Thedirection and magnitude of this current is such that it produces atorque on the T-shaped armature-flapper member 49, 34 so as to pivotthis member in a clockwise direction about pivotal axis 50 as viewed inFIG. 7, this direction being depicted by the arrows T. Such pivotalmovement brings the tip of flapper 34 initially hard over against theoutlet of left nozzle 36, while this tip moves farther away from rightnozzle 35. This diverts fluid flow into left spool end chamber 60, whilefurther opening the connection of right spool end chamber 59 to drain.The effect is to produce a differential pressure on valve spool 33,hydraulically driving it to the right. As this spool so moves, it dragsthe lower end of feedback spring 83, causing this spring to bend, andpulls the flapper tip away from the left nozzle. The spool will continueto displace rightwardly, and the deflection of the feedback spring willincrease, until the force exerted thereby on the flapper produces atorque which counterbalances the electrically induced torque produced bythe current input to the torque motor. When this occurs, the flapper tipwill be returned to a position between the nozzles such that essentiallyno differential pressure then exists between the spool end chambers.Actually, a small but finite differential pressure is necessary to holdthe spool in a displaced position. The drive force on the spool soceasing, it stops and remains in a displaced position (FIG. 7) to theright of its null or centered position (FIG. 1). Thus, spooldisplacement is proportional to the magnitude of torque unbalance on thearmature-flapper member, which is related to the direction and magnitudeof current input to the servovalve.

When spool 33 displaces rightwardly relative to valve sleeve 55, asdepicted in FIG. 7, left inner lobe 73 uncovers more of left meteringport 78 and right inner lobe 69 uncovers more of right metering port 76.This opening of left port 78 establishes communication between leftannular space 71, which is under supply pressure, with left actuatingport 80 and associated conduit 82. The direction of fluid flow isrepresented by the arrows P. The enlarged communication between rightmetering port 76 and central annular space 75 allows fluid to flow fromconduit 81 through right actuating port 79, through port 76 and intospace 75 to drain. Such fluid flow to drain is represented by the arrowsD.

In FIG. 7, it is assumed that no follow-up feedback movement of valvesleeve 55 has yet occurred so that the position of this sleeve relativeto the valve body 37 is the same as depicted in FIG. 1. In other words,schematic feedback arm 103' is in the same position relative to thevalve body in both FIGS. 1 and 7.

Turning now to FIG. 8, the servovalve controller is in the samecondition as depicted in FIG. 7 except that sleeve 54 has been shiftedrightwardly to return to a nulled or centered position relative to therightwardly displaced valve spool 33. This comes about as a result ofthe change in angular position of swashplate 19 effected by fluid flowthrough conduits 81, 82, as will now be explained.

When flow through ports 76, 78 and conduits 81, 82 in the direction ofarrows P, D is occurring, conduit 82 carries a higher pressure to pumphousing port 28 than conduit 81 connected to pump housing port 27 whichis connected to drain. This drives lower control piston 24 to the leftpushing link 30 and the lower end of swashplate 19 leftwardly, while theupper end of this swashplate pushes link 29 and control piston 22 to theright. The result is that swashplate 19 has been pivoted in a clockwisedirection about its axis 20, as viewed in FIG. 8, thus changing itsangularity and establishing a stroke for pump pistons 15. This stroke isadjustable, and hence the output of the pump in ports 21, by so varyingthe angular position of the swashplate.

As swashplate 19 changes its position from that shown in FIG. 1 to thatshown in FIG. 8, feedback lever 96' has also moved in a clockwisedirection about pivotal axis 20 to shift joint J rightwardly. This jointis connected by rigid arm 103' to valve sleeve 54. The effect is to movethis valve sleeve rightwardly to a final position shown in FIG. 8 inwhich the metering ports 76, 78 are again disposed in their normalunderlapped and overlapped condition with respect to the two inner valvespool lobes 69, 73. During the course of follow-up movement of valvesleeve 54 relative to the displaced valve spool 73, this sleeve bothshifts longitudinally, represented by X in FIG. 4, and tips rotatively,represented by Y in FIG. 4. In reality, these actual distances X and Yare very minute.

The articulated feedback mechanical connection 96', J, 103' betweenswashplate 19 and valve sleeve 54 produces a one-to-one follow-up ofthis sleeve relative to the swashplate.

A change in current input to the torque motor will produce aproportionate change in valve spool position, in turn producing a changein position of the pump stroke mechanism pistons thereby changing theangularity of the swashplate about its pivotal axis. The feedback levermoves through the same angle as the swashplate and by its articulatedconnection with the feedback arm slaves the metering port sleeve to thevalve spool.

While the operation of the electrohydraulic controller has beendescribed for a current input having a direction operative to effect aninitial clockwise pivotal motion of the armature-flapper member and aconsequent rightward displacement of the valve spool, it will beappreciated that the same sort of action takes place in oppositedirections if the current direction is reversed so that conduit 81becomes the high pressure line and conduit 82 becomes the low pressureline leading to drain.

From the foregoing, it will be seen that the embodiment illustrated anddescribed herein accomplishes the various stated objectives of theinvention.

The embodiment illustrated is the best mode contemplated at the time offiling this application for carrying out the invention. Variations andmodifications of the structure illustrated will readily occur to thoseskilled in the art without departing from the spirit of the invention.

For example, the ball and recess joint 104, 101 may be reversed on thefeedback arm 103 so that the recess is in the sleeve 55 with the ball104 on the end of the arm adjacent this sleeve, and the other end ofthis arm is rigidly connected to the feedback lever 96. This willprovide articulation at the sleeve, rather than at the lever, asillustrated.

As a further example of a contemplated modification, the two mechanicalfeedbacks associated with the two relatively movable members 33, 55 ofthe output stage 32 of the servovalve could be reversed. Thus, anysuitable two-stage electrohydraulic servovalve having a torque motorwith an armature, a first stage hydraulic amplifier, and a second stagespool and sleeve, could be arranged so that the mechanical feedback tothe armature is used to create a position of the sleeve, instead of thespool as shown, proportional to the electrical input, and the secondmechanical feedback is used to position the spool, instead of the sleeveas shown, proportional to swashplate position. More specifically, insuch a modification, the hydraulic amplifier could be arranged to drivethe sleeve, a feedback spring wire similar to wire 83 could connect thesleeve 55 to the armature 49 of the torque motor, and the articulatedfeedback, provided by lever 96 and arm 103, could be operativelyinterposed between the spool 33 and the swashplate.

Accordingly, the invention is to be measured by the scope of theappended claims and not limited to the embodiment illustrated.

What is claimed is:
 1. In hydraulic apparatus having a pivotal load,having a fluid-operated mechanism for adjusting the pivotal position ofsaid load, and also having a controller including an output stage havinga movable spool member and a movable sleeve member arranged such thatthe relative positions of said members controls the flow of hydraulicfluid with respect to said mechanism, the improvement whichcomprises:mechanical feedback means interposed between said load and oneof said members and operative to produce axial and rotative movement ofsaid member in response to pivotal movement of said load, wherebypivotal movement of said load will cause follow-up movement of said onemember to null said one member on the other of said members.
 2. Theimprovement as set forth in claim 1 wherein said apparatus furthercomprises a variable-displacement hydraulic device having a pivotalswashplate, the angled position of which controls the hydraulicperformance of said device, and wherein said load is said swashplate. 3.The improvement as set forth in claim 1 wherein said mechanical feedbackmeans includes a single joint between said load and said one member. 4.The improvement as set forth in claim 3 wherein said single jointincludes a substantially spherically-surfaced ball mounted for movementwith one of said one member and load, and a substantially cylindricalrecess mounted for movement with the other of said one member and load,and wherein said ball is arranged in said recess.
 5. The improvement asset forth in claim 3 wherein said mechanical feedback means includes alever mounted fast to said load for movement therewith and having a freeend portion, and an arm mounted fast to said one member for movementtherewith and having a free end portion, and wherein said single jointis provided between said lever and arm free end portions.
 6. Theimprovement as set forth in claim 5 wherein said single joint includes asubstantially spherically-surfaced ball provided on one of said free endportions, a substantially cylindrical recess provided in the other ofsaid free end portions, and wherein said ball is arranged in saidrecess.
 7. In hydraulic apparatus .Iadd.having a casing, .Iaddend.havinga pivotal load .Iadd.arranged within said casing.Iaddend., having afluid-operated mechanism .Iadd.arranged within said casing .Iaddend.foradjusting the pivotal position of said load, and also having acontroller .Iadd.arranged without said casing, said controller.Iaddend.including an output stage having a movable spool member and amovable sleeve member arranged such that the relative positions of saidmembers controls the flow of hydraulic fluid with respect to saidmechanism, the improvement which comprises:mechanical feedback meansinterposed between said load and one of said members and operative toproduce .[.followup.]. .Iadd.follow-up .Iaddend.movement of said onemember in response to pivotal movement of said load, said mechanicalfeedback means .[.including.]. .Iadd.providing .Iaddend.a single jointbetween said load and said one member .Iadd.and including a shaft havingone end connected to said load for rotative movement therewith, havingan intermediate portion sealingly penetrating said casing, and havingits other end arranged without said casing, and including an arm havingone end connected to said one member and having its other end at alocation eccentric from the axis of said shaft.Iaddend..
 8. Theimprovement as set forth in claim 7 wherein said apparatus furtherincludes a variable-displacement hydraulic device having a pivotalswashplate, the angled position of which controls the hydraulicperformance of said device, and wherein said load is said swashplate. 9.The improvement as set forth in claim 7 wherein said single jointincludes ball and recess means.
 10. The improvement as set forth inclaim 9 wherein said ball and recess means includes a substantiallyspherically-surfaced ball mounted for movement with one of said onemember and load, and a substantially cylindrical recess mounted formovement with the other of said one member and load, and wherein saidball is arranged in said recess.
 11. The improvement as set forth inclaim 10 wherein said mechanical feedback means includes a lever mountedfast to said load for movement therewith and having a free end portion,and wherein said recess is provided in said lever free end portion..Iadd.
 12. The improvement as set forth in claim 7 wherein said arm oneend is mounted fast to said one member. .Iaddend..Iadd.
 13. Theimprovement as set forth in claim 7 wherein said single joint isprovided between said shaft and said arm other end. .Iaddend..Iadd. 14.The improvement as set forth in claim 13 wherein said single jointincludes ball and recess means. .Iaddend.